CN111536175A

CN111536175A - Piston type retarding braking system for truck

Info

Publication number: CN111536175A
Application number: CN202010569973.2A
Authority: CN
Inventors: 王永林; 郑卫国; 王明智
Original assignee: Qingdao Linda Science And Technology Development Co ltd
Current assignee: Qingdao Linda Science And Technology Development Co ltd
Priority date: 2020-06-21
Filing date: 2020-06-21
Publication date: 2020-08-14
Anticipated expiration: 2040-06-21
Also published as: CN111536175B

Abstract

The invention discloses a piston type slow-speed braking system for a truck, which relates to the technical field of vehicle braking. The piston type brake replaces the existing drum brake, so that the defect of the existing drum brake is overcome.

Description

Piston type retarding braking system for truck

Technical Field

The invention relates to the technical field of vehicle braking, in particular to a piston type retarding braking system for a truck.

Background

A vehicle brake system refers to a series of special devices that apply a certain force to certain parts of the vehicle (mainly the wheels) so as to apply a certain degree of forced braking thereto. The braking system has the following functions: the running automobile is forced to decelerate or even stop according to the requirement of a driver; stably parking a stopped vehicle under various road conditions (including on a slope); the speed of the vehicle running on the downhill is kept stable. In the prior art, drum brakes are generally adopted for braking large trucks, and have many defects, such as poor heat dissipation performance, when a long downhill is met, heat accumulation can be caused by long-time braking, and a wheel drum is easy to generate extremely complex deformation under the influence of high temperature, so that brake recession and vibration and shake phenomena are easy to generate, and the brake efficiency is reduced; and the drum brake has heavier overall mass and more use amount, and is not favorable for the light weight of the vehicle.

Disclosure of Invention

Aiming at the defects in the prior art, the invention aims to provide a piston type retarding braking system for a truck, which overcomes the defects of the existing drum brake by replacing the existing drum brake with a piston type brake.

In order to achieve the purpose, the invention provides the following technical scheme: the utility model provides a piston retarding braking system for truck which characterized in that: a piston type slow-speed braking system for a truck comprises an engine, a power shaft for transmitting the power of the engine, a gearbox for receiving the power shaft for transmission, a disc brake arranged on the power shaft, a rear axle and a piston type brake for braking the rear axle; the transmission case is provided with a transmission shaft which transmits the rotating speed after the variable speed output of the transmission case to the rear axle; the piston type brake comprises a piston and a connecting mechanism which is mechanically connected with the rear axle or the transmission shaft and transmits the resistance of the piston; the piston comprises a sleeve, a piston block which is tightly abutted against the inner wall of the sleeve and is connected to the inner wall of the sleeve in a sliding mode, a piston rod fixed on one side of the piston block, and a ball valve fixed at one end, far away from the piston rod, of the sleeve, wherein a driving piece for driving the ball valve to move is arranged on the ball valve.

By adopting the technical scheme, when the brake is not operated, the piston block in the sleeve does piston motion; during the braking, the driving piece drives the ball valve to work, the opening that the control ball valve is close to the one end of ball valve with the sleeve reduces or closes completely, piston motion is done to the piston piece this moment, and the piston piece can compress the gas between piston piece and the ball valve, increases the resistance that the piston piece removed, and the resistance that the piston piece removed passes through coupling mechanism and transmits for the transmission shaft, reduces the rotational speed of rear axle, brakes the vehicle. When the vehicle is completely braked, the hand brake for stopping the vehicle is realized through a disc brake arranged in the cab. The piston type brake has smaller mass, so that the lightweight of braking is convenient to realize; and when the piston brake meets continuous downhill, the brake quality can not be reduced due to heat accumulation caused by long-time braking, the occurrence of locking in the braking process can be reduced, and the defect of a drum brake is overcome.

The invention is further configured to: the connecting mechanism comprises a gear lack which coaxially rotates with the transmission shaft and a movable frame arranged on the periphery of the gear lack; the number of the pistons is even, the pistons are symmetrically arranged at two ends of the moving frame, and piston rods positioned at two ends of the moving frame are fixedly connected with the moving frame; the top and the bottom of the inner wall of the movable frame are respectively fixed with a lower rack and an upper rack which are meshed with the gear lacking, and the gear lacking can be meshed with the lower rack or the upper rack when rotating.

Through adopting above-mentioned technical scheme, lack the gear and rotate and drive and remove the frame and do reciprocating motion to drive the piston piece and move in the sleeve, produce the resistance of motion when the ball valve is closed, through the cooperation of lacking gear and removal frame, the motion of the piston piece of being convenient for.

The invention is further configured to: the rear axle comprises a right output shaft, a left output shaft, a driven gear, a right half axle gear, a left half axle gear and a planetary gear, wherein the right half axle gear rotates coaxially with the right output shaft and is positioned at one end of the right output shaft close to the left output shaft, the left half axle gear rotates coaxially with the left output shaft and is positioned at one end of the left output shaft close to the right output shaft, and the planetary gear is meshed with the right half axle gear and the left half axle gear simultaneously; a supporting frame is fixed on a wheel disc of the driven gear, and the planetary gear is rotationally connected with the supporting frame; the main gear is meshed with the driven gear, and the piston brake further comprises a first brake gear connected with the rear axle gear and a crankshaft driven by the first brake gear; the piston also comprises a connecting block which is fixed at one end of the piston rod close to the crankshaft and is hinged with the crankshaft.

The invention is further configured to: the first brake gear is meshed with the driven gear.

Through adopting above-mentioned technical scheme, first brake gear and driven gear meshing, during the braking, the resistance transmission of piston is for driven gear, and the resistance through driven gear operation reduces the output rotational speed of left output shaft and right output shaft, realizes the braking of vehicle.

The invention is further configured to: fourth brake gears which rotate coaxially with the left output shaft and the right output shaft are arranged on the left output shaft and the right output shaft; the first brake gear is meshed with the fourth brake gear.

Through adopting above-mentioned technical scheme, first brake gear and fourth brake gear mesh, through directly transmitting the resistance of piston for left output shaft and right output shaft, realize the braking of vehicle.

The invention is further configured to: : the number of the pistons on the piston type brake is at least two, and the connecting blocks on the plurality of piston rods are sequentially connected to the connecting rod necks adjacent to the crankshaft.

Through adopting above-mentioned technical scheme, a plurality of pistons that are in under different states can increase the production of resistance to improve the braking effect to the vehicle.

The invention is further configured to: a limiting plate is fixed at one end, close to the crankshaft, of the sleeve, a limiting hole for the piston rod to pass through is formed in the limiting plate, and an air vent is formed in the limiting plate.

By adopting the technical scheme, the limiting plate and the limiting hole limit the movement of the piston rod, the forces in other directions of the piston rod are balanced, and the movement stability of the piston rod is improved; the air vents balance the air pressure on the left side and the right side of the limiting plate, and influence on vehicle operation is reduced.

The invention is further configured to: the sleeve is close to the one end intercommunication of ball valve has the intake pipe, and the telescopic one end intercommunication is kept away from to the intake pipe has the electromagnetic directional valve, and one side of electromagnetic directional valve is provided with the air pump for the sleeve gas injection.

By adopting the technical scheme, when emergency braking occurs, the ball valve is closed at the moment; before the piston block compresses the gas in the sleeve, the gas tank is filled with the gas through the electromagnetic directional valve, and the gas pressure in the sleeve is increased, so that the resistance of the piston block in motion is increased, and the emergency braking effect is increased.

The invention is further configured to: the sleeve is communicated with an air outlet pipe and an air pipe, and the air outlet pipe and the air pipe are respectively communicated with a first electromagnetic valve and a second electromagnetic valve.

Through adopting above-mentioned technical scheme, at the in-process of ordinary operation or ordinary brake, the gas in the sleeve can enter into the gas pitcher through the outlet duct, aerifys in the gas pitcher. When the emergency brake is performed, gas in the gas tank enters the sleeve through the vent pipe to pressurize the sleeve.

The invention is further configured to: and an oil cut-off switch is arranged on the oil inlet pipe.

By adopting the technical scheme, when a long downhill is encountered in the driving process, the oil supply of the engine is cut off through the oil cut-off switch, the oil wasted by the idling rotation of the engine is reduced, and the oil-saving effect is realized.

In conclusion, the beneficial technical effects of the invention are as follows:

1. when the brake is not operated, the piston block in the sleeve does piston motion; during the braking, the driving piece drives the ball valve work, and the control ball valve reduces or closes completely the opening that the sleeve is close to the one end of ball valve, and piston motion is done to the piston piece this moment, and the piston piece can compress the gas between piston piece and the ball valve, increases the resistance that the piston piece removed, and the resistance that the piston piece removed received passes through the bent axle and transmits for the rear axle to reduce the output rotational speed of left output shaft and right output shaft, brake the vehicle. When the vehicle is completely braked, the hand brake for stopping the vehicle is realized through a disc brake arranged in the cab. The piston type brake has smaller mass, so that the lightweight of braking is convenient to realize; when the piston brake encounters continuous downhill, the brake quality is not reduced due to heat accumulation caused by long-time braking, the occurrence of locking in the braking process can be reduced, and the defects of a drum brake are overcome;

2. the pistons in different states can increase the generation of resistance, so that the braking effect on the vehicle is improved;

3. when emergency braking occurs, the ball valve is closed at the moment; before the piston block compresses the air in the sleeve, the air pump leads the air into the sleeve through the electromagnetic directional valve to increase the air pressure in the sleeve, thereby increasing the resistance of the movement of the piston block and increasing the effect of emergency braking.

Drawings

FIG. 1 is a schematic overall structure diagram according to a first embodiment;

FIG. 2 is a schematic view of a piston brake according to an embodiment;

FIG. 3 is a schematic view of the piston;

FIG. 4 is a schematic view of the overall structure of the second embodiment;

FIG. 5 is a schematic structural view of an embodiment of a rear axle;

FIG. 6 is a schematic structural diagram of a two-piston brake according to an embodiment

FIG. 7 is a schematic view showing the construction of a piston;

FIG. 8 is a schematic view of the overall structure of the third embodiment;

FIG. 9 is a schematic structural view of a three-piston brake embodying an embodiment;

FIG. 10 is a schematic structural view of a four-piston embodiment;

FIG. 11 is a schematic structural view of a fifth engine according to an embodiment;

FIG. 12 is a schematic structural view of a sixth piston according to an embodiment.

In the figure: 1. an engine; 11. an oil inlet pipe; 12. a fuel cut-off switch; 2. a power shaft; 3. a gearbox; 31. a drive shaft; 32. a main gear; 4. a disc brake; 5. a rear axle; 51. a housing; 52. a right output shaft; 521. a connecting disc; 53. a left output shaft; 54. a driven gear; 541. a support frame; 55. a right half shaft gear; 56. a left side gear; 57. a planetary gear; 6. a piston brake; 61. a first brake gear; 62. a brake shaft; 63. a second brake gear; 64. a third brake gear; 65. a crankshaft; 651. a support; 66. a piston; 661. a sleeve; 6611. a limiting plate; 6612. a limiting hole; 6613. a vent hole; 662. a piston block; 663. a piston rod; 664. connecting blocks; 665. a ball valve; 6651. a micro motor; 666. an air inlet pipe; 667. an electromagnetic directional valve; 668. a gas tank; 6681. a connecting pipe; 67. a connecting frame; 68. a fourth brake gear; 69. a housing; 7. a frame body; 71. a gear is missing; 72. moving the frame; 721. a lower rack; 722. an upper rack; 8. an air outlet pipe; 81. a first solenoid valve; 9. a breather pipe; 91. a second solenoid valve.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings.

The first embodiment is as follows: a piston type slow-speed braking system for a truck comprises an engine 1, a power shaft 2 driven by the engine 1 to rotate, a gearbox 3, a transmission shaft 31 for outputting the rotating speed of the gearbox 3 after being changed, a disc brake 4 arranged on the transmission shaft 31, a rear axle 5 arranged at one end of the power shaft 2 far away from the engine 1, and a piston type brake 6 for braking the transmission shaft 31. The rear axle 5 is provided with a connection plate 521 to be connected to a tire.

Referring to fig. 2 and 3, the piston brake 6 includes a frame 7 fixed to a vehicle body and a piston 66 fixed to the frame 7.

The transmission shaft 31 is provided with a missing gear 71 (connected by a key way) which coaxially rotates with the transmission shaft 31, the periphery of the missing gear 71 is provided with a movable frame 72 which is matched with the missing gear 71, and the top end and the bottom end of the inner wall of the movable frame 72 are respectively fixed with a lower rack 721 and an upper rack 722 which are meshed with the missing gear 71. When the missing gear 71 rotates, it can engage with the lower rack 721 or the upper rack 722, so as to drive the moving frame 72 to reciprocate. The number of the pistons 66 is an even number, and the pistons are symmetrically arranged at both ends of the moving frame 72.

Piston 66 includes a sleeve 661 fixed to frame 7, a piston block 662 closely abutting against an inner wall of sleeve 661 and slidably coupled to the inner wall of sleeve 661, a piston rod 663 fixed to piston block 662 on a side closer to drive shaft 31, and a ball valve 665 provided at an end of sleeve 661 remote from drive shaft 31.

The piston rods 663 at both ends of the moving frame 72 are fixedly connected to the moving frame 72 at the ends close to the moving frame 72, and can support the moving frame 72 and restrict the vertical displacement of the moving frame 72. When the missing gear 71 rotates, the reciprocating moving frame 72 drives the piston block 662 connected to the piston rod 663 to reciprocate in the sleeve 661.

A limiting plate 6611 is fixed at one end of the sleeve 661 close to the transmission shaft 31, a limiting hole 6612 is formed in the limiting plate 6611, the radius of the limiting hole 6612 is the same as the radius of the piston rod 663, the piston rod 663 can penetrate through the limiting hole, and the movement of the piston rod 663 is limited. The position-limiting plate 6611 is further provided with a vent 6613, and the vent 6613 can balance the air pressure on the two sides of the position-limiting plate 6611.

The end of sleeve 661 remote from drive shaft 31 is closed by ball valve 665. The ball valve 665 is provided with a micro motor 6651 which drives the ball valve 665 to move, and the opening and closing of the ball valve 665 and the opening size of the ball valve 665 and the sleeve 661 can be controlled by controlling the rotation of the micro motor 6651, so that the piston block 662 moves in the sleeve to bear the air pressure resistance. The micro motor 6651 is controlled by a brake pedal provided in the cab.

The piston brake 6 is not limited to braking the drive shaft 31, and may be provided on another driven shaft of the truck to brake the truck.

During normal truck operation, the ball valve 665 on the piston 66 is in an open position, with the piston block 662 sliding normally within the sleeve. When the caliper needs to be decelerated or braked, oiling is stopped, and the transmission shaft 31 stops continuously providing power for the rear axle 5. The micro-motor then controls the movement of ball 665 so that the opening between ball 665 and sleeve 661 decreases, and as piston block 662 moves away from drive shaft 31, gas is not timely vented from the sleeve as piston block 662 moves, due to the now smaller opening between ball 665 and sleeve 661, so that piston block 662 compresses the gas within the sleeve. The compressed air will provide resistance to continued movement of the piston block 662, thereby reducing the kinetic energy of the movement of the piston block 662 and, in turn, the rotational speed at which the drive shaft 31 rotates. When the rotation speed of the propeller shaft 31 is reduced, the rotation speed transmitted to the rear axle 5 is reduced, and the rotation of the tire is reduced, thereby realizing the deceleration braking of the truck.

Example two: the difference between this embodiment and the first embodiment is that the piston rod 663 is driven to reciprocate in a different manner.

A piston type slow-speed braking system for a truck is shown in figure 4 and comprises an engine 1, a power shaft 2 driven by the engine 1 to rotate, a gearbox 3, a disc brake 4 arranged between the gearbox 3 and the engine 1, a rear axle 5 arranged at one end, far away from the engine 1, of the power shaft 2 and a piston type brake 6 for braking the rear axle 5. The number of the piston type brakes 6 is two groups, and the piston type brakes are symmetrically arranged at two ends of the rear axle 5. The number of disc brakes 4 is two and the control end extends into the cab of the truck.

The transmission case 3 is provided with a transmission shaft 31, the power shaft 2 transmits the power of the engine 1 to the transmission case 3, and the power is output through the transmission shaft 31 after the transmission case 3 rotates.

Referring to fig. 4 and 5, the rear axle 5 includes a housing 51 fixed to the truck body and a differential disposed inside the housing 51. The differential includes a right output shaft 52, a left output shaft 53, a driven gear 54, a right side gear 55 that rotates coaxially with the right output shaft 52 and is located at an end of the right output shaft 52 near the left output shaft 53, a left side gear 56 that rotates coaxially with the left output shaft 53 and is located at an end of the left output shaft 53 near the right output shaft 52, and planetary gears 57 that mesh with both the right side gear 55 and the left side gear 56. A supporting frame 541 is fixed to a disk of the driven gear 54, and the planetary gear 57 is rotatably connected to the supporting frame 541.

A main gear 32 which rotates coaxially with the transmission shaft 31 is fixed at one end of the transmission shaft 31 close to the rear axle 5. The main gear 32 is engaged with the driven gear 54 to transmit the power of the engine 1 to the differential, thereby rotating the right and left

output shafts

52 and 53. A connection plate 521 connected to a tire is fixed to one end of the right output shaft 52 and the left output shaft 53 away from each other.

The driven gear 54, the right side gear 55, the left side gear 56, the planetary gears 57, and the main gear 32 are all bevel gears.

Referring to fig. 5 and 6, the piston brake 6 includes a first brake gear 61 engaged with the driven gear 54, a brake shaft 62 rotating coaxially with the first brake gear 61, a second brake gear 63 rotating coaxially with the brake shaft 62, a third brake gear 64 engaged with the second brake gear 63, a crankshaft 65 rotating coaxially with the third brake gear 64, a piston 66 moved by the crankshaft 65, and a carrier 67 fixing the piston. An end of the crankshaft 65 remote from the third brake gear 64 is provided with a bracket 651 fixed to the housing 51 and supporting the crankshaft 65, and the crankshaft is rotatably connected to the bracket 651. The connecting frame 67 is fixed to the housing 51. The first brake gear 61, the second brake gear 63 and the second brake gear 63 are all bevel gears.

Referring to fig. 6 and 7, the piston 66 includes a sleeve 661 fixed to the connecting frame 67, a piston block 662 closely abutting against a side wall of the sleeve 661 and slidably coupled to an inner wall of the sleeve 661, a piston rod 663 fixed to a side of the piston block 662 close to the crankshaft 65, a connecting block 664 fixed to an end of the piston rod 663 close to the crankshaft 65 and hinged to the crankshaft 65, and a ball valve 665 provided at an end of the sleeve 661 remote from the crankshaft 65.

A limiting plate 6611 is fixed at one end of the sleeve 661 close to the crankshaft 65, a limiting hole 6612 is formed in the limiting plate 6611, the radius of the limiting hole 6612 is the same as the radius of the piston rod 663, the piston rod 663 can penetrate through the limiting hole, and the movement of the piston rod 663 is limited. The position-limiting plate 6611 is further provided with a vent 6613, and the vent 6613 can balance the air pressure on the two sides of the position-limiting plate 6611.

The end of the sleeve 661 remote from the crankshaft 65 is closed by a ball valve 665. The ball valve 665 is provided with a micro motor 6651 which drives the ball valve 665 to move, and the opening and closing of the ball valve 665 and the opening size of the ball valve 665 and the sleeve 661 can be controlled by controlling the rotation of the micro motor 6651, so that the piston block 662 moves in the sleeve to bear the air pressure resistance. The micro motor 6651 is controlled by a brake pedal provided in the cab.

The number of the pistons 66 on one piston brake 6 is at least two, and the connecting blocks 664 on the piston rods 663 of a plurality of pistons 66 are sequentially connected to the adjacent connecting necks of the crankshaft 65, so that the piston blocks 662 of the adjacent two pistons 66 move towards the crankshaft 65 and away from the crankshaft 65 respectively.

The using method comprises the following steps: during normal truck operation, the ball valve 665 on the piston 66 is in an open position, with the piston block 662 sliding normally within the sleeve. When the caliper needs to be decelerated or braked, oiling is stopped, and the transmission shaft 31 stops continuously providing power for the rear axle 5. The micro-motor then controls the movement of the ball 665 so that the opening between the ball 665 and the sleeve 661 decreases, and as the piston block 662 moves away from the crankshaft 65, gas is not immediately exhausted from the sleeve as the piston block 662 moves, due to the smaller opening between the ball 665 and the sleeve 661, so that the piston block 662 compresses the gas. The compressed air may provide resistance to continued movement of the piston block 662, thereby reducing the kinetic energy of the movement of the piston block 662 and, in turn, the rotational speed at which the crankshaft 65 rotates. When the rotation speed of crankshaft 65 is reduced, the rotation of brake shaft 62 connected to crankshaft 65 through a gear is reduced. When the rotation speed of the brake shaft 62 is reduced, the rotation speed of the driven gear 54 meshing with the first brake gear 61 is reduced, and the rotation speed of the differential is reduced to reduce the rotation speed of the tire, thereby realizing the deceleration braking of the truck.

Because the conventional brake adopts a drum brake, if an anti-lock system is not arranged, the locking condition can occur in the emergency brake. And in the piston type brake 6, even if the ball valve 665 is completely closed, the resistance of the movement of the piston block 662 is increased, and the piston block 662 can still move in the sleeve 661, so that the occurrence of tire locking is reduced, and the braking safety is improved.

Example three: the difference between this embodiment and the first embodiment is the braking position of the piston brake 6.

Referring to fig. 5 and 6, the left output shaft 53 (and the right output shaft 52) is provided with a fourth brake gear 68 that rotates coaxially with the left output shaft 53 (and the right output shaft 52), and the first brake gear 61 is meshed with the fourth brake gear 68. A housing 69 supporting the first brake gear 61, the brake shaft 62, and the second brake gear 63 is fixed to the housing 51. At this time, the resistance of the piston 66 is directly transmitted to the left output shaft 53 (and the right output shaft 52), and the left output shaft 53 (and the right output shaft 52) is directly decelerated and braked.

Example four: the present embodiment differs from the first and second embodiments in the difference of the piston 66.

Referring to fig. 10, an air inlet pipe 666 is communicated with one end of the sleeve 661 close to the ball valve 665, an electromagnetic directional valve 667 is communicated with one end of the air inlet pipe 666 far from the sleeve 661, an air tank 668 (high-pressure air is in the air tank 668) is arranged on one side of the electromagnetic directional valve 667, and the electromagnetic directional valve 667 is communicated with the air tank 668 through a connecting pipe 6681. When emergency braking is encountered, the ball valve 665 needs to be closed; before the piston block 662 compresses the air in the sleeve 661, the air reservoir 668 is vented through the solenoid switch valve 667 to increase the air pressure in the sleeve 661, thereby increasing the resistance to movement of the piston block 662 and increasing the effectiveness of the emergency brake.

Example five: the present embodiment differs from the first embodiment in the engine 1.

Referring to fig. 11, an oil inlet pipe 11 is communicated with the engine 1, and the oil inlet pipe 11 supplies oil to each oil cylinder of the engine. The oil inlet pipe 11 is provided with an oil cut-off switch 12, the oil cut-off switch 12 is an electromagnetic valve, and a control end is arranged in a cab. When the vehicle runs on a long downhill, the fuel cut-off switch 12 cuts off the fuel supply of the engine 1, thereby reducing the waste of fuel when the engine rotates at an idle speed and realizing the fuel-saving effect.

Example six: the difference between this embodiment and the third embodiment is the difference in the sleeve 661. Referring to fig. 12, the sleeve 661 is connected to an air outlet tube 8 and an air pipe 9, and the air outlet tube 8 and the air pipe 9 are connected to a first solenoid valve 81 and a second solenoid valve 91, respectively. The air outlet pipe 8 and the vent pipe 9 are both communicated with the air tank 668, the air outlet pipe 8 and the vent pipe 9 are both provided with one-way valves, and the one-way valves on the air outlet pipe 8 enable the air in the sleeve 661 to only flow in the direction of the air tank 668; a one-way valve in the vent line 9 allows gas to flow only from the gas tank 668 to the sleeve 661. During normal operation or normal braking, gas in the sleeve 661 can enter the gas tank 668 through the gas outlet pipe 8 to charge the gas tank 668. During a hard brake, gas in the gas tank 668 enters the sleeve 661 through the vent pipe 9 to pressurize the sleeve 661.

In the prior art, the inflator of the gas tank 668 is powered by an output shaft of the engine 1, so that the middle period of the gas tank 668 is achieved. In this embodiment, venting of the gas tank 668 is practiced by venting the gas tank 668 through a gas outlet tube 8 connected to a sleeve 661, instead of a gas charging device powered by the engine 1.

The embodiments of the present invention are preferred embodiments of the present invention, and the scope of the present invention is not limited by these embodiments, so: all equivalent changes made according to the structure, shape and principle of the invention are covered by the protection scope of the invention.

Claims

1. The utility model provides a piston retarding braking system for truck which characterized in that: the utility model provides a piston retarding braking system for truck which characterized in that: the brake system comprises an engine (1), a power shaft (2) for transmitting the power of the engine (1), a gearbox (3) for receiving the transmission of the power shaft (2), a disc brake (4) arranged on the power shaft (2), a rear axle (5) and a piston brake (6); a transmission shaft (31) for transmitting the rotating speed of the transmission case (3) after the speed change output to the rear axle (5) is arranged on the transmission case (3); the piston type brake (6) brakes the rear axle (5), the driven shaft or the transmission shaft (31);

the piston type brake (6) comprises a piston (66) and a connecting mechanism which is mechanically connected with the rear axle (5) and a driven shaft or a transmission shaft (31) and transmits the resistance of the piston (66);

the piston (66) comprises a sleeve (661), a piston block (662) which is tightly abutted against the inner wall of the sleeve (661) and is connected to the inner wall of the sleeve (661) in a sliding mode, a piston rod (663) fixed to one side of the piston block (662), and a ball valve (665) fixed to one end, far away from the piston rod (663) of the sleeve (661), of the piston rod (663), wherein a driving piece for driving the ball valve (665) to move is arranged on the ball valve (665).

2. The piston-type retarder brake system for trucks of claim 1, wherein: the connecting mechanism comprises a gear lack (71) which coaxially rotates with the transmission shaft (31) or the driven shaft and a moving frame (72) arranged on the periphery of the gear lack (71); the number of the pistons (66) is even, the pistons are symmetrically arranged at two ends of the movable frame (72), and piston rods (663) positioned at two ends of the movable frame (72) are fixedly connected with the movable frame (72); the top end and the bottom end of the inner wall of the movable frame (72) are respectively fixed with a lower rack (721) and an upper rack (722) which are meshed with the gear lack (71), and the gear lack (71) can be meshed with the lower rack (721) or the upper rack (722) when rotating.

3. The piston-type retarder brake system for trucks of claim 1, wherein: the rear axle (5) comprises a right output shaft (52), a left output shaft (53), a driven gear (54), a right half shaft gear (55) which rotates coaxially with the right output shaft (52) and is positioned at one end of the right output shaft (52) close to the left output shaft (53), a left half shaft gear (56) which rotates coaxially with the left output shaft (53) and is positioned at one end of the left output shaft (53) close to the right output shaft (52), and a planetary gear (57) which is meshed with the right half shaft gear (55) and the left half shaft gear (56) at the same time; a supporting frame (541) is fixed on a wheel disc of the driven gear (54), and the planetary gear (57) is rotationally connected with the supporting frame (541); the main gear (32) is meshed with the driven gear (54); the piston type brake (6) further comprises a first brake gear (61) connected with the rear axle (5) in a gear mode and a crankshaft (65) driven by the first brake gear (61); the piston (66) also comprises a connecting block (664) which is fixed at one end of the piston rod (663) close to the crankshaft (65) and is hinged with the crankshaft (65).

4. The piston-type retarder brake system for trucks of claim 3, wherein: the first brake gear (61) is engaged with the driven gear (54).

5. The piston-type retarder brake system for trucks of claim 3, wherein: the left output shaft (53) and the right output shaft (52) are provided with fourth brake gears (68) which rotate coaxially with the left output shaft (53) and the right output shaft (52); the first brake gear (61) is engaged with a fourth brake gear (68).

6. The piston-type retarder brake system for trucks of claim 3, wherein: the number of the pistons (66) on the piston type brake (6) is at least two, and the connecting blocks (664) on the plurality of piston rods (663) are sequentially connected to the adjacent connecting rod necks of the crankshaft (65).

7. The piston-type retarder brake system for trucks of claim 1, wherein: one end of the sleeve (661) close to the crankshaft (65) is fixed with a limiting plate (611), the limiting plate (6611) is provided with a limiting hole (6612) for the piston rod (663) to pass through, and the limiting plate (6611) is also provided with a vent hole (6613).

8. The piston-type retarder brake system for trucks of claim 1, wherein: one end intercommunication that sleeve (661) are close to ball valve (665) has intake pipe (666), and the one end intercommunication that sleeve (661) were kept away from in intake pipe (666) has electromagnetic directional valve (667), and one side of electromagnetic directional valve (667) is provided with air pump (668) for sleeve (661) gas injection.

9. The piston-type retarder brake system for trucks of claim 1, wherein: the sleeve (661) is communicated with an air outlet pipe (8) and an air pipe (9), and the air outlet pipe (8) and the air pipe (9) are respectively communicated with a first electromagnetic valve (81) and a second electromagnetic valve (91).

10. The piston-type retarder brake system for trucks of claim 1, wherein: and an oil cut-off switch (12) is arranged on the oil inlet pipe (11).